• 대한기계학회논문집
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• 제14권6호
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• pp.1621-1628
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• 1990

본 연구에서는 많은 실질적인 시스템에서, 많은 양의 복합된 전도, 대류, 복 사의 열전달 현상이 동시에 일어나기 때문에 복합된 열전달 모드가 다같이 다루어져야 만 한다. Fig.1에서 보는 바와 같이 얇은 원형휜이 튜브 주위에 무수히 부착되어 있 으며, 휜과 튜브주위를 기체가 흐르고 있다. 휜과 휜, 휜과 튜브표면, 휜과 주위환 경, 튜브표면과 주위환경 사이에서 복사 열전달 상호교환이 충분히 다루어졌다. 전 도, 대류, 복사기 동시에 일어나는 열전달 방정식은 비선형 적분-미분 방정식(nonlin- ear integro-differential equation)으로 표현된다. 온도 분포도(temperature dist- ributions), 열전달량(heat transfer rates), 휜효율(fin efficiencies), 휜유효성(f- ineffectivenesses)등이 계산되어졌고, 무차원 형태로 도표에 결과들을 제시하였다.

• 에너지공학
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• 제22권1호
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• pp.44-50
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• 2013

본 연구의 목적은 예혼합방식의 버너 앞에 소형 열교환기를 설치한 후 당량비를 변화시킬 때 NOx와 CO의 배출특성을 검토하고 열교환기 유용도와 엔트로피 생성수를 실험결과를 바탕으로 계산한 것이다. 실험결과 당량비가 증가할수록 화염온도가 높아지면서 열전달율은 상승한다. 배기가스 오염물질량과 유용도를 고려할 경우 본 실험범위에서의 적정 운전당량비는 0.75이다. 유용도를 증가시키고 엔트로피 생성량을 줄이기 위해서는 연소가스의 열전달량을 증가시켜야 하며 따라서 열교환기 면적을 증가시키는 것이 필요하다고 판단된다.

• 대한기계학회논문집B
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• 제34권5호
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• pp.531-537
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• 2010

본 연구에서는 옵셋 스트립 휜 열교환기에서 휜 형상에 대한 최적화를 수행하였다. 압력강하량은 감소시키고 열전달량을 증가시키기 위해 이 둘을 동시에 나타낼 수 있는 j/f, $j/f^{1/3}$, JF 등의 성능 인자가 고려되었다. STDQAO, PQRSM, MGA 등의 최적화 기법이 사용되었으며, MGA 를 통해 기존 옵셋 스트립 휜보다 JF 인자는 36%, 열전달 성능은 280% 향상된 최적화된 휜 형상을 제안하였다.

• 설비공학논문집
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• 제16권11호
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• pp.1044-1050
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• 2004

The present study has been conducted to develop a heat pipe heat exchanger for middle-high temperature ranged from 300 to $600^{\circ}C$. Heat transfer rate, overall heat transfer coefficient and temperature effectiveness were investigated using a heat pipe heat exchanger with Dowtherm A as working fluid. Theoretical analysis was also conducted, and the followings were obtained: (1) Heat exchange rate increased as waste gas temperature supplied to evaporator and frontal velocity in condenser increased, (2) Overall heat transfer coefficient increased by $3{\sim}7\%$ as frontal velocity in evaporator and condenser increased, (3) Temperature effectiveness was about $30\%$ in evaporator and was about $40\%$ in condenser, (4) Heat recovery rate was about $38\%$, (5) Pressure drop did not exceed $8\;mmH_{2}O$ under the running condition of $1{\sim}3Nm/s$, (6) Simulation results were corresponded with experimental results.

• 설비공학논문집
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• 제10권3호
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• pp.315-323
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• 1998

This paper contains a verification of simulation program to predict the capacity of a condenser used in car air-conditioners. Verification of simulation program is carried out with the comparison error between experiment and simulation bounds within 3.5%. The present investigation shows the results for heat transfer rates of condenser under different operating conditions, such as velocity and degree of superheat. The range of front velocity of air is 1∼5m/s. As the front velocity is increased, the heat transfer rate of condenser is largely increased at a low velocity range. In a meanwhile, heat transfer rate of condenser is almost constant in a range of velocity over 3m/s. As for the effect of inlet pressure of refrigerant on the heat transfer rate, we obtained the similar trend of heat transfer rates as like varying the front velocity, Also we have calculated the heat transfer rates with varying inlet superheats of refrigerant, the larger the superheat is, the more heat transfer rate is obtained.

• 한국추진공학회지
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• 제6권4호
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• pp.25-35
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• 2002

본 연구에서는 액체로켓의 엔진조건에 부합하는 재생냉각 시스템을 설계하는 방법을 다루었다. 정상상태에서 로켓 추력실에서의 열전달 과정은 연소가스로부터 벽면으로 대류와 복사가 이루어지고, 다시 연소실 벽을 통해 전도된 후 마지막으로 냉각제로 대류열전달 된다. criterial method와 integral method를 이용하여 열전달량을 구하고, 이를 이용하여 냉각채널을 설계하였으며, 러시아 냉각 시스템 설계 코드의 결과와 비교하였다. 복잡한 설계과정을 정형화된 logic을 구현하여 냉각 시스템 설계를 용이하게 하였으며, 설계변수를 변화시켜 얻어진 계산결과를 통하여 각 인자의 영향을 정성적으로 살펴보았다.

• 한국지열·수열에너지학회논문집
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• 제16권1호
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• pp.9-16
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• 2020

In this study, a numerical study was conducted to evaluate the performance improvement when CuO nanofluid was used in the plate heat exchanger. As a result, the heat transfer amount is increased by 5.45% when 2 vol% CuO nanofluid is used. The influence on the CuO nanofluid on the performance of heat exchanger is decreased by increasing the flow rate of working fluid. In addition, the overall heat transfer coefficient using 2 vol% CuO nanofluid decreased compared to the base fluid. However, the pressure drop and the consumption of the pump power is increased as the concentration of CuO nanofluid increased because the increase of the viscosity. These are increased up to 15.4% compared to those of the base fluid. Moreover, the performance index of CuO nanofluid is decreased by 12.6% compared to that of the base fluid.

• 설비공학논문집
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• 제15권12호
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• pp.1049-1059
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• 2003

R410A is considered as an alternative refrigerant to R22 for air conditioners. An experimental investigation was made to study the characteristics of the heat transfer and pressure drop for R410A flowing in a fin-and-tube heat exchanger used for commercial air-conditioning units. Experiments were carried out under the conditions of inlet refrigerant temperature of 6$0^{\circ}C$ and refrigerant mass flux varying from 150 to 250 kg/$m^2$s for refrigerant side. The inlet air has dry bulb temperature of 35$^{\circ}C$, relative humidity of 40% and air velocity varying from 0.68 to 1.6 m/s. Experiments show that air velocity decreased by 16% is needed for R410A than that of R22 for subcooling temperature of 5$^{\circ}C$, which resulted in air-side pressure drop decrease of 15% for R410A as compared to R22. As a consequence, in order to provide the same design condition of a condenser, the fan requires lower electric-power consumption with R410A than that with R22.

• 대한기계학회논문집
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• 제16권1호
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• pp.112-121
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• 1992

본 연구에서는 상기 연구의 연장으로서 Prandtl수가 6.05인 내부발열유체가 경사진 정사각 난류자연대류유동, 온도분포 및 열전달량의 분포를 수치적인 방법으로 예측하였다. 벽면 깅이의 1/2를 특성길이로 하는 Rayleigh수의 범위는 1*$10^{6}$ ~1*$10^{9}$ 으로 선택하였으며 경사각도는 0˚, 15˚, 30˚및 45˚로 선택하였다.

• 한국지열·수열에너지학회논문집
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• 제15권4호
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• pp.46-54
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• 2019

In this study, the performance of a shell and tube heat exchanger (STHE) and welded plate heat exchanger (WPHE) was measured experimentally. The pass numbers of the STHE was changed by 1, 2 and 4. As a result, the WPHE showed 2.1 times higher heat exchange capacity than that of the STHE. In case of pressure drop, the STHE with 1 and 2 pass number has a lower pressure drop than the WPHE, while the STHE with 4 pass presented higher pressure drop than the WPHE. The performance index considering the heat exchange capacity and pump consumption power, showed in oder of STHE_Pass1 > STHE_Pass2 > W PHE > STHE_Pass4 under the same flow rate. Therefore, when the WPHE was designed optimally under same operating condition with STHE, the maintenance fee and space can be reduced effectively by using the WPHE.